Transmission mechanism



Feb. 20, 1940. J. F. JOY

TRANSMISSION MECHANISM Original Filed June l5, 1935 H mi Islay!) rw.

gm 1 l- .2 VII Patented Feb. 2o, 1940 UNITED STATES` PATENT Applicat 2,190,925 TRANSMISSION MEcHANTsM Joseph F. Joy, Pittsburgh,` Pa., assignor to Sullivan Machinery Company, a corporation of Massachusetts ion June 15, 1935,` Serial No. 26,813 Renewed January 18, 1939 11 claims. (o1. 'i4-125.5)

.My invention relates to transmission mechanlsms, and more particularly to transmission mechanismshaving load-limiting and speed-con- 3 trolling features incident thereto.

The invention is particularly adaptable to the feeding mechanisms of coal-cutting machinery and to the operation of haulage devices, as will be `apparent I from the ensu ing description. In

the feeding of mining machinery, and particularly of the type which is movable over the mine bottom during cutting, it isi` powerful, tractive effort, but

is desirable to preclude the possibility of the exertion of excessive tractionin strains on the mechanisms, e motor, and breakage of the ments employed may be avoided.` It is also denecessary to provide at the same time it order that excessive xcessive loads on the flexible feeding ele- An object of my invention mission `mechanism having i ing features.

is to provide an improved transmission mechanism. 'Another object of my invention is to provide an improved trans'- mproved load-limit- I A further object of myr invention is to provide an improved transmission mechanism having improved means therein for providing intermittent or continuous Winding as desired.

Still another object of my in vention is to provide an improved transmission mechanism providing for a Wide range of eifectiv e speeds I by varying is to provide an improved load-limiting device having an invariable maximum and permitting speed variation through` associated parts.

Still another object of my invention is to provide `an improved mining machine feeding mechanism.

will hereinafter more fully appear.

invention is shown- I Fig. l is a view from abov embodiment of `the e, with parts broken away, showing a mining machine feeding mechanism in which the invention is incorporated,

Fig. 2 is a vertical section on the line 2f2 of Fig. 1, n h

Fig. 3 is a vertical transverse fragmentary 5 section on the plane corresponding to the `line` 3-3 of Fig. 1,

Fig. 4 is a vertical section showing details of construction and taken `on the plane of the line 4-4 of Fig. 1. 10

Referring to the drawing, it will be observed that a motor I, provided with anarmature shaft 2 carrying a driving pinion 3, drives, through an intermediate gear 4, a gear 5 which is keyed at 6 to a horizontal, longitudinally extending shaft 1. Said shaft] near its rearward end supports a worm 8 which meshes at its opposite sides with worm wheels 9 and Il! respectively. The worm wheel I9 is xedly secured to a vertical shaft I I, which carries a Worm I2 which engages and drives a worm wheel I3, suitably supported upon a transversely extending shaft I4 which is journaled in the frame of the apparatus at I5 and supports at its,opposite ends Winding elements IE and I'I, which may be connected 25? thereto under the control of mechanism having an operating handle E8 as desired. The Worm wheel 9 is connectible by afriction clutch I9, loaded as hereinafter described, toa vertical shaft 20 which carries a worm 2! engaging and 30` driving a worm Wheel 22, also supported upon the transverse shaft I4. The Worm wheels I3 and 22 `are connectible under the control of suitable ball clutches 23 and 24 operated by a shipper member 25, in driving relation With the shaft I 1S. 35

The structure so far described is substantially identical with the structure shown and described in my assignees copending Holmes application Serial No. 699,024, now matured into Patent No. 2,091,985, dated Sept. 7, 193'?.

Suitable means for loading the friction clutch I9 is provided for effecting intermittent or continuous loading of the clutch and for further providing a maximum load limit. This clutch loading apparatus includes a loading ring 39 hav- 45 ing fingers 3| adapted to press the clutch discs I together, andpressure is applicable to the loading ring through la second ring 32 supported bythe ring 30 on antifriction bearings and a clutchv shipper member having arms 39 and supported 50 by `a transversely extending, hollow, oscillating shaft 35 is adapted to apply the pressure to the ring 32 to effect actual loading of the clutch. The shaft 35 is appropriately ljournaled on a transverse shaft 35a in the frame of the appara- 55 tus, and carries at itsr end nearer the worm I2 the upwardly extending arm structure 36 in approximately right-angular relation to the plane of the shipper arms 34. The arm structure 36 carries at its upper end a pair of wear plates 37 and 38, and is open between its sides, as at 33, and between its ends, to permit the projection through itof an adjustable support structure 4'0. This support structure comprises a rod-like portion LEI guided in a sleeve ft2 carried by the frame and a forward biiurcated end 43 carrying a transverse pivot pin 44; and at its rearward end the support structure carries in xed relation thereto a collar member 45 having a projecting lipv portion 46 which projects into an annular groeve 41. in a manually rotatable, adjusting member 48 which is threadedly supported at I9 upon the exterior of a load-limiting device d which will be described in detail shortly. The pivot 44 supports'a lever member 5 lv whose forward.y extremity 52 is adapted to coact with a multi-lobed cam 53secured to the hub` 56 of' the worm wheel I3. The member i has a projecting portion et? which is adapted to engage the wearplate 33 carried by the upper'end of the relatively vertical arm 316.

The load-limiting device 5I! comprises a sleevelike body portion 5l' having a bore 58 in which a' that the spring 53 may be placed under any pre- Gil-f determined tension desired by the adjustment of the closure member BIJ, and thereafter the member to mayk be welded in position to preclude altering of the maximum compression of theI readily understood from what has been said. It'

will be obvious that so long as the moto-r drive pinion 3 is rotatedA the worm wheel I3 will be rotated and, accordingly, the `cam 53 will beV rotated. Fast feed drive of the transverse shaft I4 can be effected by shifting the shipper member 25 toward the worm wheel I3 in Fig. l, under which circumstances the drive will be as follows:

.` Motor pinion 3, idler 4, gear 5, shaft 1, worm 8,

Worm wheel Iii, worm I2, worm gear I3, shaft I4, and. either winding element When maximum slow speed is desired, the manually rotatable member 43 will be turned in a proper direction to causethe pivot pin 44 to move as far to the left as possible. r.['his will have two effects. It will cause the end 52 of the arm member '5I to move beyond the vertical plane including the axis of the cam 53 and thereby reduce the raising and lowering movement of the arm 5I, and will also move the portion 55 of the arm 5I bodily toward` the left and allow the spring 59 to force the nose 63 toward the left, and thereby, through the pressure of the nose 63 upon the wear plate'fill, cause the arm 36 to swing the shaft 35 and with itthe clutch shipper 34 continuously into clutch-loading relation. At this ltime the spring 5G will be under somewhat greater compression than would be the case were the collar II` against the shoulder 65, but in the design I6 or Il desired.`

of the machine the amount of this increase may be predetermined and the sealing of the spring in its container when under a fixed pressure will automatically effect an absolute control of the maximum load which can` be applied to the clutch.

In order to diminish the absolute rate of rotation of the shaft ;-I4, the" member' 4I may be moved toward the right inFig. 4 by rotation of the handle member 48, and as the pivot pin 44 is moved toward the right the end 52 is moved bodily towardthefright and engagement of the portion 55 with the wear plate 38 takes place for increasingly-` substantial periods, the further to the right the member 4| is moved. When the memberllfl is infextreme right-hand position the application,A of thelvload to the clutch I9 may be completelyl interrupted, or made any minimum desired', depending upon the range of adjustment of the member 4I permitted. In practice it is customary to providea range of adjustment suchl that' the portion l5'5 mayengage the wear plate. continuously and force the arm 36 at all times, even when the portion 52 is in the troughs of the cam 53, to such a position that the shipper member 34 can not load the clutch I9.

From the foregoing description it will be evident that the apparatus disclosed provides a continuous fast speed drive, and a slow speed drive Varying fromva certain maximum, uniform rate.

ofrotation, at which rate a maximum tension can be transmitted to thefeeding elements, down, `by reason ofl the interruptions of drive for varying periods, to a state ofcomplete interruption of drive.. At allftimes the pressure which may be applied to the friction clutch I9 is completely limited, and, without kactually deliberately breaking open the spring container, the operator is unable to take any action which might result in an overload of ythe motor, or breaking the ropes or other flexible feeding` elements; and moreover there is always insured an adequate pressure to be appliedr to the clutch discs to insure effective clutch engagement `with a I ninim-um` wear due to slippage.

While there is in this application specically described onel form which the invention may assume in practice,y it. will be understood that this form of the same is shown fory purposes of illustration and that the invention may be modified and embodied in various other forms without departing from its spirit or the scope of the appended claims.

What I claim as newrand desire to secure by Letters Patent ist' '1. In combination, a driving member, a driven member, a friction clutch' operative when loaded to connect said members for coaxial equiangular rotation, a lever swingable about a stationary pivot to load said clutch, yieldable means having a fixed point of reaction for applying loading pressure to said lever ,whereby the clutch is loaded by said yieldable` means through said lever, said yieldable means having a predeterminedlylimited maximum pressure application, a continuously rotated cam, a lever pivotally movable thereby and having a portion effective on predetermined movements, thereof to force said rst mentioned lever against' the pressure oi said yieldable means into clutch unloading position, and means for altering the fulcrum point of said second mentioned lever to vary its action on said rst'mentioned lever and thereby the duration of loading ofv said clutch by said rst mentioned lever. f

" pressure to said lever wherebythe clutch is loaded by said yieldable means through said lever, `said yieldable means having al predeterminedlylimited maximum pressure application, a continuously rotated cam turning at an angular rate substantially less than the `rate of rotation of `said driving member, a lever pivotally movable thereby and having a portion `effective on prede termined movements thereof to force said rst mentioned lever againstthe pressure of said yieldable means into clutch unloading position. and means for altering the fulcrum point of said second mentioned lever to vary its action on said first mentioned lever and thereby the duration of loading of said clutch by said first mentioned lever. y

3. In a transmission mechanism, a driving member,` a driven member, a friction clutch for connecting said members in driving relation, yieldable meansset at a predetermined pressure for applying said clutch under alpredetermined load, means associated with said clutch applying means for releasing said clutch against the action of said yieldable clutch applying means at predetermined timed intervals including a cam continuously rotatable during drive of said driving member and a lever actuated by said cam and engaging `said clutchapplying means at a point intermediate its fulcrum and its cam-engagingend, and means associated with saidA last mentioned means for varying said timed intervals of clutch release including means for varying the iulcrum point of said lever.

4. In a transmission mechanism, a driving member, va driven member, a friction clutch for connecting said members in driving relation, means for yieldably applying said clutch under a predetermined load including clutch actuating means and a coil spring acting on said clutch actuating means, and means for releasing said clutch against the action of said yieldable means at predetermined timed intervals including a cam continuously rotatable during drive of said driving member, a lever actuated by said cam and engaging said clutch actuating means at a point intermediate its fulcrum and its cam-engagingn end, and means associated with said last mentioned means for varying the time intervals of clutch release includingmeans for adjusting the iulcrum point of said lever.

5. In an intermittent unidirectional transmission mechanism, a driving element, a driven element, a friction clutch for connecting said elements in driving relation, and means for variably intermittently applying and releasing said clutch at timed intervals to effect variable intermittent unidirectional drive of said driven member inand means to vary the range of movement of said cam actuated member by said cam to vary the" range of` movement of said movably mounted member upon which said spring acts.

6. `In an intermittent unidirectional transmis sion mechanism, a drivingelement, a driven element, a friction clutch for connecting said elements in driving relation, and means for variably intermittently applying and releasing clutch at timed intervals to `effect variable intermittent unidirectional drive of said driven member `including a continuously rotating cam, yieldable clutch loading means always tending to load said Clutch including a clutch loading spring set at a predetermined maximum clutch loading pressure, said clutch loading means further including a pivoted member, and said spring acting on said pivoted member at the endtliereof remote from its pivot whereby the clutch is loaded by the spring through said pivoted member, a lever actuated by said cam for intermittently moving said pivoted clutch loading member into clutch releasing position against the action of said spring, said lever having an adjustable fulcrum and engaging said pivoted member at a pointbetween its own fulcrum and its own engagement with said cam, and means for adjusting the 'fulcrum of said lever to vary the time intervals of clutch application and release. l

7. In a transmission mechanism, coaxial relatively rotatable driving and driven members, a clutch for connecting said driven member to said driving member including cooperating clutch elements respectively rotatable with said driving and driven members, one clutch element movable along the axial line of said driving and driven members into driving engagement with said other clutch element, a `lever for moving said axially movable clutch element into driving engagement with said other clutch element, a clutch loading spring directly acting on said lever at a point spaced from the clutch-engaging-end of the latter, said spring set at a predetermined clutch loading pressure for yieldingly moving said lever into its clutch loading position whereby the clutch is loaded by said spring through said lever, means engaging said lever in opposition to Said spring for automatically swinging the lever against the pressure exerted by said spring for intermittently means associated with said last mentioned means for varying the time intervals of clutch release.

8. In a transmission mechanism, coaxial relatively rotatable driving and driven members, a clutch for connecting said driven member to said driving member including cooperating clutch elements respectively rotatable with said driving and driven members, one clutch` element mov able along the axial line of said driving and driven members into driving engagement with said other clutch element, a lever for moving said axially movable clutch element into driving engagement with said other clutch element, a clutch loading spring acting directly on said lever at a point spaced from its clutch-engagingend and set at a predetermined clutch loading pressure for yieldingly moving said lever into its clutch loading position whereby the clutch is loaded by said spring through said lever, means engaging said lever in opposition to said spring for automatically swinging the lever against the pressure exerted by said spring for intermittently releasing said axially movable clutch element irom driving engagement with said other clutch yelement at predetermined time intervals includ-k ing a rotatable cam and a lever actuated by said cam and operative to actuate said clutch applying y lever.

. ly releasing said clutch at timed intervals including a rotatable cam and a lever actuated byv said cam and engaging said clutch applying y lever in opposition to said spring, and means for varying the time intervals of clutch release including means for adjusting the fulcrum point of said second mentioned lever.

l0. In a transmission mechanism, a drive clutch, a clutch applying lever, a spring acting on said lever and set at a predetermined clutch loading pressure for urging said lever toward clutcn loading position whereby the clutch is loaded by the springthrough said lever, means connected to said lever for swinging the latter against the pressure exerted by said spring for intermittently releasing said clutch at timed intervals including a rotatable cam and a lever actuated by said cam and engaging said clutch' applying lever in opposition to said spring, and

means for varying the time intervals of clutch release including means for adjusting the fulcrum point of said second mentioned lever, said ful- Crum point adjusting means comprising an adjustable support to which said second mentioned lever is pivotally connected and means for adjusting said support.

1l. In a transmission mechanism, a drive clutch, a clutch applying lever, a spring acting on said lever for yieldingly urging the latter into clutch loading position whereby' the clutch is loaded by the spring through said lever, means acting against the pressure exerted by said spring for automatically swinging said lever intermittently to relieve the load on said clutch at predetermined timed intervals including a continuously rotating cam and a lever actuated by said cam and engaging said rst mentioned lever in opposition to said spring, and means for adjusting the fulcrumpoint of said secondmentioned lever to vary the time intervals of clutch release.

JOSEPH F. JOY. 

